Guiding device for the vane assemblies of a fluid handling device



Dec. 10, 1968 K. EICKMANN 3,415,197

GUIDING DEVICE FOR THE VANE ASSEMBLIES OF A FLUID HANDLING DEVICEOriginal Filed Dec. 5, 1963 4 Sheets-Sheet 1 Fig.

68/5 5 III II 638 K 66/5 111 II INVENTOR KARL E/CKMAN/V BY 1AM 6' MMATTORNEY Dec. 10, 1968 K. EICKMANN GUIDING DEVICE FOR THE VANEASSEMBLIES OF A FLUID HANDLING DEVICE Original Filed Dec. 5, 1963 4Sheets-Sheet 2 I NVENTOR KARI E ICKMAMV BY a: 4 g J1 ATTORNEY Dec. 10,1968 K. EICKMANN GUIDING DEVICE FOR THE VANE ASSEMBLIES OF A FLUIDHANDLING DEVICE 5, 1963 4 Sheets-Sheet 5 Original Filed Dec.

INVENTOR ATTORNEY United States Patent 3,415,197 GUIDING DEVICE FOR THEVANE ASSEMBLIES OF A FLUID HANDLING DEVICE Karl Eickmann, 2420 Isshiki,Hayama-machi, Kanaga'wa-ken, Japan Original application Dec. 5, 1963,Ser. No. 328,395, now

Patent No. 3,320,898, dated May 23, 1967. Divided and this applicationMay 22, 1967, Ser. No. 640,108

'15 Claims. (Cl. 103136) ABSTRACT OF THE DISCLOSURE The vane assembliesof a fluid handling device have turnable control pins with end portionsaxially projecting from the other parts of the respective vane assemblyand guided along endless guide tracks matching the outline of an endlessinner casing face along which the radially outer parts of the vaneassemblies move during rotation of the rotor in which the vaneassemblies are mounted.

Reference to a related application The present application is adivisional application of the copending application Ser. No. 328,395,now US. Patent 3,320,898.

Background of the invention It is known to provide fluid handlingmachines with guide means radially inward of the vanes for forcing thevanes outward during rotation of the rotor in which the vanes aremounted. In accordance with the prior art, only machines whose rotorshave no radially projecting end walls are provided with such guidemeans. This type of machine is not capable of working at high power andefficiency because the vanes have the tendency to be deformed by highpressure which causes leakage losses.

On the other hand, vane machines according to my earlier patents, forexample U.S. Patent 2,975,716, are capable of operating at high powerand efliciency, because the rotors thereof have end walls and slots inthe center rotor portion as well as in the end walls for guiding thevanes.

In fluid handling machines of the type disclosed in my earlier Patent2,975,716, it is not possible to provide guide means for guiding thevanes for outward movement in the slots of the rotor. This is due to thefact that especially at low speed of the rotor, the vane assemblies arenot pressed tightly enough against the inner endless face of the casingmember so that a tight seal between the intervane spaces could not beobtained. As a result, machines of this type do not smoothly start.

Summary 0 the invention It is the main object of the present inventionto overcome this disadvantage of high power fluid handling devices, andto provide a fluid handling machine of the type having vane end portionsguided in end members of the rotor, with control means by which thevanes are urged outward.

Another object of the invention is to use a pivot pin provided in a vaneassembly as disclosed in my prior Patent 3,158,103 for cooperation withguide tracks by which the vane assemblies are urged outwardly.

In accordance with one embodiment of the invention, each vane assemblyis composed of a plurality of vane parts including a control part, suchas a pivot pin, whose end portions are located outwardly of non-circularguide tracks sliding on the same so that the vane assemblies are movedoutwardly along the endless inner face of a casing Patented Dec. 10,1968 member by which the inward movement of the vane assemblies isaccomplished.

The endless guide tracks are either provided on the casing means, or onguide portions supported by a noncircular shaft which passes through acentral bore in the rotor, and has an end portion secured to thestationary casing means of the machine.

The novel features which are considered as characteristic for theinvention are set forth in particular in the appended claims. Theinvention itself, however, both as to its construction and its method ofoperation, together with additional objects and advantages thereof, willbe best understood from the following description of specificembodiments when read in connection with the accompanying drawings.

Brief description of the drawing FIG. 1 is an axial sectional view takenon line II in FIGS. 2 and 3, and illustrating a first embodiment of theinvention;

FIG. 2 is a cross-sectional view taken on line IIII in FIG. 1;

FIG. 3 is a cross-sectional view taken on line IIIIII in FIG. 1;

FIG. 4 is an axial sectional view taken on line IVIV in FIG. 5 andillustrating a second embodiment of the invention;

FIG. 5 is a cross-sectional view taken on line VV in FIG. 4; and

FIG. 5B is an enlarged cross-section illustrating a detail of FIG. 5within the circle BB in FIG. 5.

Description of the preferred embodiments Referring first to theembodiment of FIGS. 1 to 3, an outer stator casing means includes twoparts 601A and 601 and supports a casing member 608 having an endlessinner non-circular face 612 and being provided with a fluid inlet 679and a fluid outlet 680. Rotor means are mounted in bearings of thecasing means and including a shaft portion 622, a center rotor portion602 and radially outwardly projecting end members which embrace lateralend faces of the casing member 608 and form with the same and the rotorcenter portion 602, a working space which is divided into intervanespaces by vane assemblies mounted in radial slots 657 extending into theend members of the rotor. Vane assemblies are respectively mounted inthe slots of the rotor means for radial movement, each vane assemblyincluding an inner part guided in the respective slot, a pivot pin 610,and a shoe 611 pivotally mounted on pivot pin 610 and sliding on theinner endless face 612 in sealing contact.

The device illustrated in FIGS. 1 to 3 is preferably a combustion engineto which a fuel-and-air mixture is supplied through the inlet port 679to enter the intervane spaces 625A or 625B. The fuel-air mixture iscompressed when the respective intervane space reaches the position625C. Compression continues when the intervane space reaches position625D. In the position of the intervane spaces 625D in FIG. 2, or 625E inFIG. 3, the compression is so great that the fuel-air mixture is heatedto a temperature higher than its ignition temperature so that thefuel-air mixture starts combustion without the aid of additionalignition means.

After the intervane space has reached the position 625E, expansion ofthe intervane space takes place due to the expansion of the combustiongases, and is continued until the intervane spaces pass throughpositions 625F and 6256 whereupon the burnt gases are discharged fromintervane space 625H through outlet port 680.

As shown in FIG. 2, the casing 608 is divided into two casing parts 608Aand 608B along the dividing plane AB also designated by referencecharacter 608AB. The casing parts 608A and 608B are fastened together bybolt means 648A, 648B, 648C and 648D. Casing part 608A contains theinlet port 679, and casing part 608B contains the outlet port 680. Theouter casing means surrounds the inner casing member 608 and is fastenedto the same by bolt means 648E and 6481 Casing cooling spaces 671 areprovided in casing memher 608, and are surrounded or closed by the outercasing 601. Casing seals 601A and 601B are provided for sealing thecooling space 671 between casing 601 and casing member 608. Casing ribs676 for transferring heat extend into the cooling space 671.

Beds 637, seats 638, seats 639, spring means 651, outer beds 633, innerbeds 632, outer seals 634, inner seals 635, casing covers 631 andsealing faces 688 are provided for sealing the working space. Supportrings 604A and 6048 are provided and held in place by snap rings. Therotor means include a central rotor part 602, rotor end members 604 and605 with inner annular faces 613 and 614 which are in sliding engagementwith the lateral faces of inner casing member 608.

The vane assemblies 609, or vane parts 643 and 644 are provided withseals 645 inserted into the respective seal beds 645A. The seal beds645A extend over the whole length of the center part of the vane andalso extend to to the axial vane end portions 615 and 616 which arelocated in slot portions of the end members of the rotor and have radialextensions 619 and 620. Vane seal 645 is provided with seal faces 645Bor 645C. Due to the effective sealing of vane seals 645, leakage betweenthe intervane spaces is prevented.

In accordance with the invention, non-circular endless guide tracks 47are provided on the parts 601A and 601B of the outer casing 601 forguiding slide members 46, 7

best seen in FIG. 1 which are turnably mounted on the end portions ofpivot pin 610. Pivot pin 610 and the slide members 46 are a control partof the vane assembly by which the vane assembly is moved outwardly dueto the outline of the guide tracks 47. Since slide members 46 areturnable on the end portions of pins 611, they follow the contour of theguide tracks 47. Axial separation of slide members 46 from pins 611 isprevented by the sliding abutment of the axial end face of the slidemembers 46 on an enless face 47A of the respective casing part 601A or601B.

During rotation of the rotor, slide members 46 slide along the guidetracks 47, or roll along the same if members 46 are constructed asrollers having bores 46A for receiving the end portions of pins 610. Theguide tracks 47 have such a configuration that the control part 610, 46of the vane assembly 609, 643, 644, 610, or 611 are forced to moveoutward in radial direction so that the shoe 690 of the respective vaneassembly slides along the inner casing face 612 in tight sealingengagement. When the shoes 690 move along portions of the endless innerface 612 where the intervane spaces are reduced in size, the vaneassemblies are moved inwardly by the inner endless face 612. The actionof the guide tracks 47 prevents the sticking of the vane assemblies inthe respective slots during expansion of the intervane spaces. Suchsticking of the vane assemblies may happen due to deformation of a vanepart or the rotor slot, or due to friction of the sealing means.Evidently, the follower parts 46 could ,be constructed not only as slideor rollers, but also as ball or roller bearings.

Guide tracks 47B are provided outwardly of guide tracks 47 for guidingslide members 46 inwardly together with the vane assembly, as shown inFIG 1, and also in FIG. 2 in broken lines. Guide tracks 47B perform thefunction of the inner endless face 612 for urging the vane assembliesinwardly during the contraction of the intervane spaces, but may beomitted.

The function of outer endless guide tracks 47B is to prevent too greatpressure of slide shoe 611 against the inner face 612 of easing member608. Guide tracks 47B can be designed so that a certain clearanceremains between the outer face 690 of shoe 611 and the endless innerface 612 whereby friction is reduced. Sealing means 692 of little weightmay be provided in slide shoe 611 for sealing the clearance between theouter face 690 and the inner endless face 612.

From the above description of FIGS. 1 to 3 it becomes apparent that thepresent invention provides each vane assembly with a control part 610,46 which is guided by guide track means 47, 47A, 47B for moving theouter parts of the vane assemblies along the inner endlless face 612 ofcasing member 608 which forms the intervane spaces with the vanes andthe rotor.

Referring now to the embodiment illustrated in FIGS. 4, 5 and 5B, whichillustrates a double acting rotary pump or motor, the casing means 1001Ais integral with the casing member 1008 which has an inner endless face1012. The casing is divided along radial planes into a plurality ofparts, for example into two casing halves 1001B and 1001F. The casingparts 1001E and 1001F are bolted together by bolt and nut means 1048.

The dividing face is schematically indicated at 1001G, and it is evidentthat the casing may be divided in more than two parts.

Casing covers 1001B and 1001C are parts of the composite casing 1001A.The rotor 1002 of the machine has a shaft 1062 which may be sealed bysealing means 1063. The' rotor has a center part 1002 and end walls 1004and 1005 on which lateral cover parts 1006 and 1007 abut. Cover rings1006A and 1007A surround the side walls 1004 and 1005. The side walls,covers, and rings constitute end members of the rotor which project fromthe center portion of the rotor outwardly in axial direction.

Radial slots 1057 are formed in the rotor center part 1002 and extendinto the side walls 1004 and 1005 where they are closed at the axialends by covers 1006 and 1007 and at the radially outer ends by rings1006A and 1007B. Rings 1006A and 1007A are in sliding engagement withthe lateral end faces of easing member 1008 and form with the same andthe vane assemblies sealed intervane .spaces.

The division of the end members into covers 1006, 1007, rings 1006A,1007A and side walls 1004 and 1005 considerably facilitates themanufacturing and assembly of the apparatus.

Rings 1006A and 1007A may be used for limiting outward movement of thevanes so that the clearance between the outer face 1090 of slide shoe1011 and the endless inner face 1012 of casing member 1008 can beexactly determined. The inner diameter of the rings 1006A and 1007A canbe selected that due to the deformation produced by the pressure, thevanes may move radially outwardly farther if the rings are deformed sothat the clearance between the outer face 1090 of the slide shoe and therespective portion of the endless inner face 1012 decreases when thepressure in the respective slots increases.

The clearance and corresponding leakage losses are thereby reduced.

Rotor center portion 1002 has radial slots 1057 and rotor side walls1004 and 1005 have slot extensions 1058 and 1059.

A vane means 1009 is slidably mounted in each slot and has a pivot pin1010 supporting the respective slide shoe 1011 for angular movement.Intervane spaces are formed by the vanes 1009 in the working spacebounded by the inner face 1012, rotor side walls 1004, 1005, and rotorcenter portion 1002. The intervane spaces 1025 have positions 1025A to1025F. The endless inner face 1012 of the casing member 1008 isnon-circular and has such a configuration that during rotation of therotor, each intervane space 1025 on the left of the dividing plane 1001Gincreases its volume to a maximum, and thereafter reduces its volume toa minimum. The increase and decrease of the volume of the intervanespaces is used for sucking in and discharging the fluid through entranceport 1053 and discharge port 1054.

In accordance with the invention, each vane assembly 1009, 1010, 1011 iscontrolled to move outwardly so that the faces 1090 are in any angularposition of the rotor in sliding engagement with the inner casing face1012.

Each end member, and more particularly each end wall 1004 and 1005 has aradial recess 1004A and 1005A projecting outwardly from the innercentral bore of the rotor. Covers 1006 and 1007 close recesses 1004A and1005A in axial direction.

Guide means 1046A and 1046B are located in each of recesses 1004A,1005A. Guide means 1046A and 1046B have endless guide tracks 1047A and1047B. The outline of the guide tracks corresponds to the outline of theendless inner face of easing member 1008. In accordance with theinvention, the inner endless face 1012 of the embodiment of FIG. 4, andthe inner endless face 612 of the embodiment of FIG. 1 are composed ofpart-circular face portions which considerably facilitates themanufacturing of the machine. The guide tracks 1047A, 1047B, and 47,respectively, are composed of corresponding part circular track portionsmatching the portions of the endless inner face 612 or 1012 in radiusand angular positions.

As best seen in FIG. 5, guide member 1046 extends radially outwardly tothe area where the respective intervane space has its greatest volume,and the respective guide member 1046 has a lower track portion in radialdirection where the intervance space will have a smaller volume. Asviewed in the cross section of FIG. 5, the guide members project to theright and to the left farthest in radial direction, and are narrower inthe direction of the plane 1001G. This is due to the fact that thegreatest volume of the intervane spaces is assumed in a horizontalplane, and the smallest volume is assumed in a vertical plane.

The dimensions and configuration of the guide members and of the guidetracks 1047A, 1047B must be very accurately observed during manufacturein order to guide and push the vanes 1009 in radial outward direction toa position cooperating with the endless inner face 1012 of the casingmember 1008. If the accuracy is insuflicient, a clearance causingexcessive leakage losses would appear between the outer slide face 1090of vane part 1011 and the endless inner face 1012.

FIG. 5 shows different constructions for alternate vane means. One vanemeans has an outer shoe 1090 mounted for pivotal movement by means of apivot pin 1010 on the vane part 1009 which has at the inner end a radialrecess receiving a vane portion 10000 with a open bearing recess inwhich a control pin 1009D is mounted for angular movement. Springs 1051in recess 1009B abut vane parts 1009 and 1009C to urge control pin 1009Dinward so that the end portions of the control pin abut the guide tracks1047A and 1047B. The construction of the alternate vanes issubstantially the same, but instead of the shoe 1090, two pins 1011X and1011Y are provided at the outer end of the vane part 1009Z, as alsoshown in FIG. 5B. Slide pins 1011X and 1011Y have flat slide faces 1090'sliding on the inner surface 1012. A small chamber 1011G is foamedbetween the slide pins 1011X and 1011Y, each of which is capable ofturning the angle alpha for following the curvature of the endless innerface 1012 of casing member 1008.

In both vane constructions, the control part 1009D slides on the guidetracks 1047A, 1047B for moving the vane outward and into contact withthe inner face 1012. Due to the fact that the end portions of controlpart 1009D slide on the guide tracks, they transmit a force tending torotate guide members 1046A, 1046B. Therefore, guide members 1046A, 1046Bmust be mounted within the turning motor in such a manner that theycannot rotate due to engagement by the control part and also by lateralfaces of rotor end walls 1004, 1005 and rotor covers 1006 and 1007.

In accordance with the invention, stationary mounting means are providedin the central bore of the rotor. The mounting means includes a shafthaving a thick portion 1046D, and a thin portion 1046D'. Portion 1046Bis secured to a portion of the stator casing and prevented by a pin1001Z from turning movement. The thin shaft portion passes throughcentral openings in guide members 1046A and 1046B and ends in the regionof the end cover 1007. The shaft portion 1046D has two flat faces 104615and 1046F, and the inner openings of the guide members have acorresponding slot-shape to fit on the faces 104613 and 1046F wherebyturning movement of the guide members is prevented, and the same aresecurely mounted within the radial recesses 1004A and 1005A of therotor.

It is evident that any other non-circular shape of the mounting shaft,or a splined mounting shaft would accomplish the same purpose. The rotoris mounted by means of shaft 1062 in the bearing portion 1063 of theouter casing, and also by means of a hub portion of end cover 1006 onthe mounting shaft portion 1046D. The vane parts 1009Z have radialprojections 1015 and 1016 at the axial ends thereof which partly embracethe casing member 1008, as best seen in FIG. 4. In this manner axialguidance of the vanes is obtained. Due to the fact that the controlparts 1009B, 1009C can move into and out of the recesses 1009B whileengaging the guide tracks 1047A, 1047B, a sliding of slide pins 1011Xand 1011Y on the endless inner face 012 is assured. Members 1011X, 1011Yperform an angular movement in the corresponding grooves of vane part10092 while sliding along portions of different curvature of the innerendless face 1012.

Control pin 1009D may slide on the guide tracks, but could be providedwith rollers or slide blocks turnably mounted on control pin 1009D, asdescribed with reference to FIG. 1. Spring means 1051 compensate smallinaccuracies between the outline of the guide tracks and of the endlessinner casing face 1012. The inward travel of the vanes is obtained bythe configuration of the endless inner face 1012 in the regions wherethe intervane spaces are reduced in volume.

It will be understood that each of the elements described above may alsofind a useful application in other types of fluid handling machinesdiffering from the type described above.

While the invention has been illustrated and described as embodied in aguiding device for vane assemblies, it is not intended to be limited tothe illustrated embodiments, since various modification and structuralchanges may be made without departing from the spirit of the invention.

What is claimed as new and desired to be secured by Letters Patent isset forth in the appended claims.

I claim:

1. In a fluid handling device, in combination, casing means including acasing member having a non-circular endless inner face and lateral endfaces and inlet and outlet means for a fluid; rotor means mounted insaid casing means for rotation about an axis, and including a centralrotor portion located within said endless inner face and two end membersprojecting in radial direction from said central rotor portion andhaving a greater diameter than the same and said endless inner face,said end members having endless lateral peripheral faces being,respectively, located opposite at least portions of said lateral endfaces embracing the same in sliding and sealing contact whereby aworking chamber for said fluid is formed between said rotor means andsaid endless inner face of said casing member, said rotor means beingformed with a set of slots located in radial planes and extending inaxial direction in said central rotor portion and into said end members;a set of vane assemblies respectively mounted in said slots for radialmovement into and out of said slots for dividing said working chamberinto a set of intervane spaces sealed fromeach other, each vane assemblybeing composed of a plurality of vane parts aligned in radial directionand including a control part; and guide means supported on said casingmeans and having non-circular guide track means whose outline matchesthe outline of said endless inner face, said guide track means beingdisposed radially inward of said control part and guiding the same andsaid vane means in outer radial direction during rotation of said rotormeans so that said vane assemblies move along said endless inner face.

2. A device as claimed in claim 1 wherein said control part includes apin having axially projecting end portions, and wherein said guide meansinclude two non-circular endless guide tracks respectively locatedradially inwards of said end portions in sliding contact with the samefor guiding said pins and said vane assemblies.

3. A device as claimed in claim 1 wherein said control part includes apin having axially projecting end portions, and slide members mountedfor turning movement on said end portions; and wherein said guide meansinclude two non-circular endless guide tracks respectively locatedradially inwards of said slide members for guiding the same, said pins,and said vane assemblies.

4. A device as claimed in claim 1 wherein each vane assembly includes anouter part located outward of said control part in radial direction andformed at the radially inner end thereof with a guide recess for guidingsaid control part.

5. A device as claimed in claim 4 and including spring means in saidguide recess abutting said outer part and said control part so that saidouter part can move relative to said control part.

6. A device as claimed in claim 1 wherein said endless inner face ofsaid casing member is composed of a plurality of part-cylindrical curvedinner face portions; and wherein said guide track means are endless andare composed of a plurality of part cylindrical curved outer trackportions whose radii of curvature and angular positions correspond tothose of said inner face portions.

7. A device as claimed in claim 6 wherein said end members of said rotormeans include end walls formed with openings; and wherein said controlpart has end portions projecting from the other parts of the vaneassembly through said openings and beyond said end walls in axialdirection; and wherein said guide means include two guide tracks locatedoutward of said end walls in axial direction and respectivelycooperating with said end portions of said control part for guiding saidvane assemblies toward said endless inner face.

8. A device as claimed in claim 1 wherein said control part includes apin having axially projecting end portions, and wherein said guide meansinclude two non-circular guide tracks respectively located inward ofsaid end portions of said pins of said vane assemblies; wherein eachvane assembly includes an inner part guided in the respective slot and ashoe part cooperating with said endless inner face of said casingmember; and wherein the central portion of said pin mounts said shoepart on said inner part for angular movement.

9. A device as claimed in claim 8 and including slide members turnablymounted on said end portions of each of said pins and slidingly engagingsaid guide tracks.

10. In a fluid handling device, in combination, casing means including acasing member having a non-circular endless inner face and lateral endfaces, and inlet and outlet means for a fluid, rotor means mounted insaid casing means for rotation about an axis, and including a centralrotor portion located within said endless inner face and two end membersprojecting in radial direction from said central rotor portion andhaving a greater diameter than the same and said endless inner face,said end members having endless lateral peripheral faces being,respectively, located opposite at least portions of said lateral endfaces embracing the same in sliding and sealing contact whereby aworking chamber for said fluid is formed between said rotor means andsaid endless inner face of said casing member, said rotor means beingformed with a set of slots located in radial planes and extending inaxial direction in said central rotor portion and into said end members,said rotor means being formed with an axial bore extending through saidcentral rotor portion and through one of said end members, and at leastpartly into the other end member, and also formed with at least onerecess extending from said central bore in radially outward directioninto at least one of said end members; mounting means secured to saidcasing means and located in said central bore; guide means including anoncircular endless guide track means matching the outline of saidendless inner face, said guide means being fixedly mounted on saidmounting means and located in said recess; and a set of vane meansrespectively mounted in said slots for radial movement into and out ofsaid slots for dividing said working chamber into intervane spaces, eachvane means including a control part slidably guided on said endlessguide track means for guiding said vane means in outer radial directionso that said vane means move along said endless inner face.

11. A device as claimed in claim 10 wherein each end member is formedwith a recess projecting from said central bore in outward radialdirection; wherein said guide means include two guide portions havingnoncircular guide tracks matching the outline of said endless innerface, said guide portions being fixed on said mounting means and beingrespectively located in said recesses; and wherein said control part ofeach vane means has two end portions respectively located radiallyoutward of said guide tracks and guided along the same.

12. A device as claimed in claim 11 wherein each vane means includes aradially outer part; and wherein said control part is guided in saidradially outer part for radial movement and has end portions axiallyprojecting from the same.

13. A device as claimed in claim 12 wherein each vane means includesspring means between said outer part and said control part.

14. A device as claimed in claim 13 wherein said outer part of said vanemeans has a guide recess; wherein each control part includes a slidepart guided in said guide recess, and a pin turnably mounted on saidslide part and having end portions projecting from the same and fromsaid outer part and engaging said guide tracks.

15. A device as claimed in claim 11 wherein said control part includes apin mounted on said vane means for turning movement and engaging saidguide track means.

References Cited UNITED STATES PATENTS 1,153,874 9/1915 Shore 230-1521,488,729 4/1924 Ballay 103-136 2,264,616 12/1941 Buckbee 230-1522,688,924 9/1954 Links.

2,975,716 3/1961 Eickmann 103-136 3,062,151 11/1962 Eickmann 103-1363,285,190 11/1966 Eickmann 103-136 3,320,897 5/1966 Eickmann 103-136FRED C. MATTERN, 111., Primary Examiner.

WILBUR J. GOODLIN, Assistant Examiner.

